US7047750B2 - Pulse tube refrigerating machine - Google Patents

Pulse tube refrigerating machine Download PDF

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Publication number
US7047750B2
US7047750B2 US10/486,355 US48635504A US7047750B2 US 7047750 B2 US7047750 B2 US 7047750B2 US 48635504 A US48635504 A US 48635504A US 7047750 B2 US7047750 B2 US 7047750B2
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Prior art keywords
pulse tube
temperature
pressure source
refrigerant
wall
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US10/486,355
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US20050044860A1 (en
Inventor
Hideo Mita
Tetuya Gotou
Motohiro Igarasi
Takayuki Furusawa
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Central Japan Railway Co
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Aisin Seiki Co Ltd
Central Japan Railway Co
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Assigned to CENTRAL JAPAN RAILWAY COMPANY, AISIN SEIKI KABUSHIKI KAISHA reassignment CENTRAL JAPAN RAILWAY COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FURUSAWA, TAKAYUKI, GOTOU, TETUYA, IGARASI, MOTOHIRO, MITA, HIDEO
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Assigned to CENTRAL JAPAN RAILWAY COMPANY reassignment CENTRAL JAPAN RAILWAY COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AISIN SEIKI KABUSHIKI KAISHA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • F25B9/145—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle pulse-tube cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1408—Pulse-tube cycles with pulse tube having U-turn or L-turn type geometrical arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1412—Pulse-tube cycles characterised by heat exchanger details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1414—Pulse-tube cycles characterised by pulse tube details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1418—Pulse-tube cycles with valves in gas supply and return lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1424—Pulse tubes with basic schematic including an orifice and a reservoir
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • F25D19/006—Thermal coupling structure or interface

Definitions

  • the present invention relates to a pulse tube refrigerator comprising a pulse tube connected to a cold reservoir and having a hot end that generates heat.
  • a conventional pulse tube refrigerator (Japanese Patent Application Laid-Open (kokai) No. 8-271071) is constructed as shown in FIG. 14 .
  • a high-pressure port 108 a of a pressure vibration source 101 is connected to a main changeover valve 111 , and a port 111 h of the main changeover valve 111 communicates with a cold reservoir 103 , a heat absorber 104 , and a pulse tube 105 via a heat radiating unit passage 112 .
  • a hot end 105 c of the pulse tube 105 is connected, through flow-rate adjustment means 122 , to a first heat transfer tube 116 having a tubular shape and a port 106 p of a phase adjustment changeover valve 106 .
  • the phase adjustment changeover valve 106 is connected to the high-pressure port 108 a and a low-pressure port 108 b of the pressure vibration source 101 .
  • the above conventional pulse tube refrigerator when refrigerant flows from the phase adjustment changeover valve 106 into the hot end 105 c of the pulse tube 105 via the flow-rate adjustment means 122 , the refrigerant undergoes adiabatic compression, whereby the gas temperature within the pulse tube increases, and the wall temperature of the pulse tube 105 elevates to about 120° C. in a range extending from the hot end 105 c of the pulse tube 105 to a longitudinally central portion of the pulse tube. Accordingly, the above conventional pulse tube refrigerator has a problem in that heat of the hot gas within the pulse tube 105 and heat of the wall of the pulse tube 105 are conducted to a cold end of the pulse tube 105 , to thereby lower refrigeration capacity.
  • the above conventional pulse tube refrigerator has a problem in that the free gas space increases, thereby decreasing the refrigeration capacity of the refrigerator.
  • the present inventor has conceived a technical idea of the present invention such that, in a pulse tube refrigerator having a pulse tube connected to a cold reservoir and having a hot end that generates heat, a high-temperature-side portion on the wall of the pulse tube is cooled by means of cooling medium which is lower in temperature than the high-temperature-side wall portion of the pulse tube.
  • the present invention provides a pulse tube refrigerator which comprises a pulse tube connected to a cold reservoir and having a hot end that generates heat, and cooling means for cooling a high-temperature-side portion on the wall of the pulse tube by use of cooling medium which is lower in temperature than the high-temperature-side portion on the wall of the pulse tube.
  • the present invention according to the first invention provides a pulse tube refrigerator in which the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use or refrigerant of the pulse tube refrigerator.
  • the present invention according to the first invention provides a pulse tube refrigerator in which the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of atmospheric air.
  • the present invention according to the second invention provides a pulse tube refrigerator in which the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant which flows out of a pressure source and flows into the cold reservoir.
  • the present invention according to the second invention provides a pulse tube refrigerator in which the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant which flows between a discharge port of a pressure source and a high-pressure inlet port of a changeover valve communicating with the discharge port of the pressure source.
  • the present invention according to the second invention provides a pulse tube refrigerator in which the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant which flows out of the cold reservoir and flows into a pressure source.
  • the present invention according to the second invention provides a pulse tube refrigerator in which the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant which flows between a low-pressure outlet port of a changeover valve and a suction port of a pressure source.
  • the present invention according to the second invention provides a pulse tube refrigerator in which the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant from a compressor provided separately.
  • the present invention according to the second invention provides a pulse tube refrigerator in which the cooling means cools a heat radiating unit disposed at the hot end of the pulse tube, by use of refrigerant which flows between a discharge side of a pressure source and a high-pressure inlet port of a changeover valve communicating with the discharge side of the pressure source.
  • the present invention according to the second invention provides a pulse tube refrigerator in which the cooling means cools a heat radiating unit disposed at the hot end of the pulse tube, by use of refrigerant which flows between a suction port of a pressure source and a low-pressure outlet port of a changeover valve communicating with the suction port of the pressure source.
  • the present invention according to the second invention provides a pulse tube refrigerator in which a radiator is provided between a suction port of a pressure source and a low-pressure outlet port of a changeover valve communicating with the suction port of the pressure source; the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant flowing out of the low-pressure outlet port of the changeover valve; and the refrigerant used to cool the high-temperature-side portion on the wall of the pulse tube is cooled by use of the radiator.
  • the present invention according to the second invention provides a pulse tube refrigerator in which a radiator is provided between a suction port of a pressure source and a low-pressure outlet port of a changeover valve communicating with the suction port of the pressure source; the cooling means cools a heat radiating unit disposed at the hot end of the pulse tube by use of refrigerant flowing out of the low-pressure outlet port of the changeover valve; and the refrigerant used to cool the heat radiating unit is cooled by use of the radiator.
  • the present invention according to the third invention provides a pulse tube refrigerator in which the cooling means is constituted by a high-temperature-side portion on the wall of the pulse tube disposed in the atmosphere.
  • the present invention according to the thirteenth invention provides a pulse tube refrigerator in which fins are provided on an outer circumferential surface of the high-temperature-side portion on the wall of the pulse tube disposed in the atmosphere.
  • the present invention according to the thirteenth invention or the fourteenth invention provides a pulse tube refrigerator in which air is forcedly supplied to the high-temperature-side portion of the wall of the pulse tube.
  • the present invention according to the thirteenth invention provides a pulse tube refrigerator in which the high-temperature-side portion on the wall of the pulse tube disposed in the atmosphere is formed of a member having good heat conduction; a low-temperature-side portion on the wall of the pulse tube disposed within a vacuum tank is formed of a member having poor heat conduction; and the high-temperature-side portion and the low-temperature-side portion are joined together.
  • the present invention according to the thirteenth invention provides a pulse tube refrigerator in which one end of a conducting member is disposed in thermal contact with the high-temperature-side portion on the wall of the pulse tube, and the other end of the conducting member is disposed in thermal contact with a cooling source which is lower in temperature than the high-temperature-side portion on the wall of the pulse tube.
  • the present invention according to the seventeenth invention provides a pulse tube refrigerator in which the cooling source is formed of a vacuum tank of the refrigerator.
  • the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of cooling medium which is lower in temperature than the high-temperature-side portion on the wall of the pulse tube. Therefore, the pulse tube refrigerator of the present invention accomplishes the effect of increasing the refrigerating capacity.
  • the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant of the pulse tube refrigerator. Therefore the pulse tube refrigerator of the second invention accomplishes the effect of increasing the refrigerating capacity as a result of a decrease in the quantity of heat which reaches a cold end of the pulse tube because of movement of refrigerant gas.
  • the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of atmospheric air. Therefore, the pulse tube refrigerator of the third invention accomplishes the effect of increasing the refrigerating capacity.
  • the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant which flows out of the pressure source and flows into the cold reservoir. Accordingly, in the pulse tube refrigerator of the present invention, when refrigerant flows from a phase adjuster to the pulse tube, the gas temperature at the high-temperature side of the pulse tube increases; and refrigerant flows from the phase adjuster toward the pulse tube in synchronism with the timing at which refrigerant flows out of a pressure source and flows into the cold reservoir.
  • the pulse tube refrigerator of the fourth invention accomplishes the effect of increasing the refrigerating capacity.
  • the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant which flows between a discharge port of a pressure source and the high-pressure inlet port of the changeover valve communicating with the discharge port of the pressure source. Therefore, in the pulse tube refrigerator of the present invention, the high-temperature-side wall portion of the pulse tube and refrigerant at the high-temperature side of the pulse tube are cooled, and such cooling is effected by use of refrigerant flowing between a discharge port of the pressure source and an inflow side of the changeover valve.
  • the pulse tube refrigerator of the present invention accomplishes the effect of increasing the refrigerating capacity effectively.
  • the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant which flows out of the cold reservoir and flows into a pressure source. Therefore, in a pulse tube refrigerator of the sixth invention, the timing of cooling the high-temperature side of the pulse tube shifts by about 180° as compared with the above-described fourth invention.
  • refrigerant flowing into the pressure source is lower in temperature than refrigerant flowing into the hot end of the cold reservoir, because refrigerant flowing out of the hot end of the cold reservoir flows into the pressure source. Therefore, the temperature of refrigerant which cools the high-temperature side wall portion of the pulse tube is low.
  • the pulse tube refrigerator of the sixth invention accomplishes the effect of increasing the refrigerating capacity.
  • the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant which flows between the low-pressure outlet port of a changeover valve and a suction port of the pressure source. Therefore, the pulse tube refrigerator of the seventh invention is the same as that of the above-described sixth invention in terms of the action of cooling the high-temperature-side portion on the wall of the pulse tube and cooling the high-temperature side of the pulse tube via the wall.
  • the pulse tube refrigerator of the seventh invention accomplishes the effect of increasing the refrigerating capacity effectively.
  • the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant from a compressor provided separately. Therefore, in the pulse tube refrigerator of the above-described eighth invention, pressure loss and temperature increase of the refrigerant, which would otherwise occur when the high-temperature-side portion on the wall of the pulse tube is cooled by used of refrigerant of the pressure source, do not occur, and thus the high-temperature side of the pulse tube can be cooled. Therefore, the pulse tube refrigerator achieves the effect of increasing the refrigerating capacity to the greatest extent.
  • the cooling means cools a heat radiating unit disposed at the hot end of the pulse tube, by use of refrigerant which flows between a discharge side of a pressure source and a high-pressure inlet port of a changeover valve communicating with the discharge side of the pressure source. Therefore, the pulse tube refrigerator of the ninth invention is the same as that of the above-described fourth invention in terms of the action of cooling the high-temperature-side portion on the wall of the pulse tube and cooling the high-temperature side of the pulse tube through the wall.
  • the heat radiating unit is cooled by use of refrigerant flowing from the discharge port of the pressure source, so that the free gas space between the changeover valve and the hot end of the cold reservoir does not increase.
  • the pulse tube refrigerator of the ninth invention accomplishes the effect of increasing the refrigerating capacity effectively.
  • the cooling means cools a heat radiating unit disposed at the hot end of the pulse tube, by use of refrigerant which flows between a suction port of a pressure source and a low-pressure outlet port of a changeover valve communicating with the suction port or the pressure source. Therefore, in the pulse tube refrigerator of the above-described tenth invention, since cooling is performed by use of refrigerant which flows between the suction port of the pressure source and the outlet side of the changeover valve, the heat radiating unit is cooled by refrigerant flowing to the suction port of the pressure source, so that the free gas space between the changeover valve and the hot end of the cold reservoir does not increase. Moreover, the pulse tube refrigerator of the tenth invention accomplishes the effect of increasing the refrigerating capacity effectively.
  • the cooling means cools the high-temperature-side portion on the wall of the pulse tube by use of refrigerant flowing out of the low-pressure outlet port of the changeover valve; and the refrigerant used to cool the high-temperature-side portion on the wall of the pulse tube is cooled by use of the radiator provided between a suction port of a pressure source and a low-pressure outlet port of a changeover valve communicating with the suction port of the pressure source. Therefore, the pulse tube refrigerator of the present invention accomplishes the effect of increasing the refrigerating capacity effectively.
  • the cooling means cools a heat radiating unit disposed at the hot end of the pulse tube by use of refrigerant flowing out of the low-pressure outlet port of the changeover valve, and the refrigerant used to cool the heat radiating unit is cooled by use of the radiator provided between a suction port of a pressure source and a low-pressure outlet port of a changeover valve communicating with the suction port of the pressure source. Therefore, the pulse tube refrigerator of the present invention accomplishes the effect of increasing the refrigerating capacity effectively.
  • the cooling means is constituted by a high-temperature-side portion on the wall of the pulse tube disposed in the atmosphere. Therefore, in the pulse tube refrigerator of the above-described thirteenth invention, since the wall temperature at the high-temperature side of the pulse tube decreases because of air cooling of the high-temperature-side portion on the wall of the pulse tube, the quantity of heat which reaches the cold end of the pulse tube due to heat conduction decreases, and refrigerant gas in contact with the inner wall surface of the high-temperature-side portion of the pulse tube is also cooled, whereby the quantity of heat which reaches the cold end of the pulse tube due to movement of the refrigerant gas also decreases. Moreover, the pulse tube refrigerator of the thirteenth invention accomplishes the effect of increasing the refrigerating capacity.
  • the pulse tube refrigerator of the fourteenth invention having the above-described construction according to the thirteenth invention, fins are provided on an outer circumferential surface of the high-temperature-side portion on the wall of the pulse tube disposed in the atmosphere. Therefore, in the pulse tube refrigerator of the above-described fourteenth invention, the cooling area of the pulse tube is increased so as to increase the degree of cooling by air, whereby the temperature of the high-temperature-side wall portion of the pulse tube decreases. Moreover, the pulse tube refrigerator of the present invention accomplishes the effect of increasing the refrigerating capacity.
  • the pulse tube refrigerator of the fifteenth invention having the above-described construction according to the thirteenth invention or the fourteenth invention, air is forcedly supplied to the high-temperature-side portion of the wall of the pulse tube. Therefore, in the pulse tube refrigerator of the above-described fifteenth invention, the heat transfer of air which cools the high-temperature-side wall portion of the pulse tube is improved so as to increase the degree of cooling by air, whereby the temperature of the high-temperature-side wall portion of the pulse tube decreases. Moreover, the pulse tube refrigerator of the fifteenth invention accomplishes the effect of increasing the refrigerating capacity.
  • the high-temperature-side portion on the wall of the pulse tube disposed in the atmosphere is formed of a member having good heat conduction; a low-temperature-side portion on the wall of the pulse tube disposed within a vacuum tank is formed of a member having poor heat conduction; and the high-temperature-side portion and the low-temperature-side portion are joined together.
  • the pulse tube refrigerator of the above-described sixteenth invention since the heat conduction in the radial direction of the high-temperature-side tube portion of the pulse tube disposed in the atmosphere increases, the temperature difference between the inner circumferential surface and the outer circumferential surface of the high-temperature-side tube portion decreases, whereby the temperature of refrigerant in contact with the inner circumferential surface decreases, and accomplishes the effect of increasing the refrigerating capacity.
  • one end of a conducting member is disposed in thermal contact with the high-temperature-side portion on the wall of the pulse tube, and the other end of the conducting member is disposed in thermal contact with a cooling source which is lower in temperature than the high-temperature-side portion on the wall of the pulse tube. Therefore, the high-temperature-side wall portion of the pulse tube is cooled by heat conduct, and the pulse tube refrigerator of the present invention accomplishes the effect of increasing the refrigerating capacity.
  • the cooling source is formed of a vacuum tank of the refrigerator. Therefore, in the pulse tube refrigerator of the above-described eighteenth invention, heat which moves from the high-temperature-side portion of the pulse tube to the vacuum chamber via the conducting member is radiated to the atmosphere at the outer circumferential surface of the vacuum tank, whereby the high-temperature-side wall portion of the pulse tube is cooled. Moreover, the pulse tube refrigerator of the present invention accomplishes the effect of increasing the refrigerating capacity.
  • FIG. 1 is a circuit diagram showing the pulse tube refrigerator of the first embodiment according to the present invention.
  • FIG. 2 is a circuit diagram showing the pulse tube refrigerator of the second embodiment according to the present invention.
  • FIG. 3 is a circuit diagram showing the pulse tube refrigerator of the third embodiment according to the present invention.
  • FIG. 4 is a circuit diagram showing the pulse tube refrigerator of the fourth embodiment according to the present invention.
  • FIG. 5 is a circuit diagram showing the pulse tube refrigerator of the fifth embodiment according to the present invention.
  • FIG. 6 is PV diagrams at the low temperature and high-temperature sides, respectively, of the pulse tube according to the embodiment of the present invention.
  • FIG. 7 is a circuit diagram showing the pulse tube refrigerator of the sixth embodiment according to the present invention.
  • FIG. 8 is a circuit diagram showing the pulse tube refrigerator of the seventh embodiment according to the present invention.
  • FIG. 9 is a circuit diagram showing the pulse tube refrigerator of the eighth embodiment according to the present invention.
  • FIG. 10 is a circuit diagram showing the pulse tube refrigerator of the ninth embodiment according to the present invention.
  • FIG. 11 is a circuit diagram showing the pulse tube refrigerator of the tenth embodiment according to the present invention.
  • FIG. 12 is a circuit diagram showing the pulse tube refrigerator of the eleventh embodiment according to the present invention.
  • FIG. 13 is a circuit diagram showing four concrete examples of the phase adjuster of the embodiment according to the present invention.
  • FIG. 14 is a circuit diagram showing a conventional pulse tube refrigerator.
  • a pulse tube refrigerator includes a pulse tube 11 , which is connected to a cold reservoir 9 , and has a hot end 11 a that generates heat.
  • Cooling means 30 is provided so as to cool a high-temperature-side wall portion 11 cd of the pulse tube by means of cooling medium having a temperature lower than a high-temperature-side wall temperature of the pulse tube.
  • the high-temperature-side wall portion 11 cd of the pulse tube is cooled by means of refrigerant, flowing out of a pressure source 1 of the pulse tube refrigerator and flowing into the cold reservoir 9 .
  • a discharge port 1 a of the pressure source 1 communicates with a high-pressure inlet port 7 a of a changeover valve 7 via a flow passage 2 , a flow passage 3 , a flow passage 4 , a flow passage 5 , and a flow passage 6 , in this sequence.
  • a suction port 1 b of the pressure source 1 is connected to a low-pressure outlet port 7 b of the changeover valve 7 via a flow passage 18 .
  • the flow passage 3 which partially constitutes the cooling means 30 , is disposed in contact with an outer surface of the high-temperature-side wall portion 11 cd of the pulse tube so as to establish thermal contact with and cool the high-temperature-side wall portion 11 cd , the high-temperature-side wall portion extending from a point 11 d at which the temperature of the pulse tube 11 is higher than atmospheric temperature to a point 11 c near the hot end of the pulse tube 11 .
  • the flow passage 5 which partially constitutes the cooling means 30 , is disposed in contact with an outer surface of a heat radiating unit 12 disposed at the hot end 11 a of the pulse tube 11 , in such a manner that the flow passage 5 establishes thermal contract with the outer circumferential surface of the heat radiating unit 12 and thus exchanges heat with refrigerant flowing within the heat radiating unit 12 .
  • the changeover valve 7 is controlled to be switched in such a manner that a port 7 c of the changeover valve 7 communicates with the high-pressure inlet port 7 a when refrigerant flows from the pressure source 1 to the cold reservoir 9 , and communicates with the low-pressure outlet port 7 b when refrigerant flows from the cold reservoir 9 to the pressure source 1 .
  • the cold reservoir 9 is filled with a cold-reserving material 9 c such as wire gauze.
  • the port 7 c communicates with a hot end 9 a of the cold reservoir 9 via a flow passage 8 .
  • a cold end 9 b of the cold reservoir 9 communicates with a cold end 11 b of the pulse tube 11 via a flow passage 10 .
  • the hot end 11 a of the pulse tube 11 communicates with a phase adjuster 14 via the heat radiating unit 12 and a flow passage 13 .
  • Reference numeral 15 denotes a vacuum tank, the interior of which is maintained at vacuum.
  • the pulse tube refrigerator is configured in the above-described manner.
  • Refrigerant compressed at the pressure source 1 is cooled by means of a compressor cooler 100 .
  • FIG. 6 shows PV diagrams at the low temperature and high-temperature sides, respectively, of the pulse tube according to the first embodiment.
  • a compression step Ia in which the port 7 c of the changeover valve 7 communicates with neither the high-pressure inlet port 7 a nor the low-pressure outlet port 7 b , refrigerant flows from the phase adjuster 14 to the hot end 11 a of the pulse tube 11 via the flow passage 13 and the heat radiating unit 12 , whereby the pressure within the pulse tube 11 increases from a low pressure to an intermediate pressure, and the temperature of refrigerant increases.
  • a compression step Ib ( FIG. 6 ) in which the port 7 c of the changeover valve 7 communicates with the high-pressure inlet port 7 a , refrigerant flowing out of the high pressure port 1 a of the pressure source 1 flows into the cold end 11 b of the pulse tube 11 via the flow passage 2 , the flow passage 3 , the flow passage 4 , the flow passage 5 , the flow passage 6 , the changeover valve 7 , the cold reservoir 9 , and the flow passage 10 , in this sequence. Meanwhile, refrigerant flowing out of the phase adjuster 14 flows into the hot end 11 a of the pulse tube 11 via the flow passage 13 and the heat radiating unit 12 . As a result, refrigerant within the pulse tube 11 is compressed from the almost intermediate pressure to a substantially high pressure, and the temperature of refrigerant within the pulse tube 11 further increases.
  • the compression step Ia and the compression step Ib constitute the compression step I.
  • a substantially-isobaric step II ( FIG. 6 ), which follows the compression step I and in which the port 7 c of the changeover valve 7 communicates with the high-pressure inlet port 7 a , refrigerant flows from the pressure source 1 to the cold end 11 b of the pulse tube 11 , while passing through the changeover valve 7 , the cold reservoir 9 , and the flow passage 10 . Meanwhile, refrigerant flows from the hot end 11 a of the pulse tube 11 to the phase adjuster via the heat radiating unit 12 and the flow passage 13 . As a result, the pressure of refrigerant becomes slightly higher than that at the end of the compression step I, and the temperature of refrigerant becomes slightly higher than that at the end of the compression step I.
  • an expansion step IIIb ( FIG. 6 ) in which the port 7 c of the changeover valve 7 communicates with the low-pressure outlet port 7 b , refrigerant flows from the cold end of the pulse tube to the low-pressure side of the pressure source 1 via the flow passage 10 , the cold reservoir 9 , the changeover valve 7 , and the flow passage 8 . Meanwhile, refrigerant flows from the hot end 11 a of the pulse tube 11 into the phase adjuster 14 via the heat radiating unit 12 and the flow passage 13 . As a result, the pressure of refrigerant decreases from the substantially intermediate pressure to an almost low pressure, and the temperature of refrigerant within the pulse tube 11 further decreases.
  • the expansion step IIIa and the expansion step IIIb constitute the expansion step III.
  • a substantially-isobaric step IV which follows the expansion step III and in which the port 7 c of the changeover valve 7 communicates with the low-pressure output port 7 b , low-pressure refrigerant flows from the cold end 11 b of the pulse tube 11 to the suction side of the pressure source 1 via the flow passage 10 , the cold reservoir 9 , the flow passage 8 , the changeover valve 7 , and the flow passage 8 . Meanwhile, low-pressure refrigerant flows from the hot end 11 a of the pulse tube 11 into the phase adjuster 14 via the heat radiating unit 12 and the flow passage 13 . As a result, the pressure of refrigerant becomes slightly lower than that at the end of the expansion step III, and the temperature of refrigerant within the pulse tube 11 becomes slightly lower than that at the end of the expansion step III.
  • refrigerant within the pulse tube 11 performs work (L 1 ) and in the above-described substantially-isobaric step IV and compression step I, refrigerant within the pulse tube 11 receives work (L 2 ).
  • the difference between the work (L 1 ) and the work (L 2 ) is equal to a refrigerating quantity (Qi) generated at the low-temperature side of the pulse tube 11 .
  • Refrigerant flowing through the flow passage 3 cools the high-temperature-side wall portion 11 cd of the pulse tube 11 , and the high-temperature-side wall portion 11 cd captures heat from a portion of refrigerant in contact with the inner surface of the high-temperature-side wall portion 11 cdb to thereby lower the temperature of the refrigerant.
  • the above-described refrigerant flowing into the pulse tube 11 from the low-temperature side thereof flows through the hot end 11 a thereof to the phase adjuster 14 via the heat radiating unit 12 and the flow passage 13 .
  • Such refrigerant is cooled when passing through the heat radiating unit 12 by refrigerant which flows through the flow passage 5 . Since the flow passage 5 is disposed between the changeover valve 7 and the pressure source 1 , the free gas spaces of the flow passage 8 , the cold reservoir 9 , the flow passage 10 , the pulse tube 11 , the heat radiating unit 12 , and the flow passage 13 do not increase, and the decrease in refrigerating capacity is small.
  • a pulse tube refrigerator according to a second embodiment which is another embodiment belonging to the second, fourth, fifth, ninth, and tenth inventions, differs from that of the first embodiment shown in FIG. 1 in that the circuit between the discharge port 1 a of the pressure source 1 and the high-pressure inlet port 7 a of the changeover valve 7 consists of a main circuit and a branch circuit.
  • the main circuit extends from the discharge port 1 a of the pressure source 1 to the high-pressure inlet port 7 a of the changeover valve 7 via a flow passage 2 a , a flow-rate adjustment valve 19 , and a flow passage 2 b .
  • the branch circuit branches off from the flow passage 2 a , and merges into the flow passage 2 b after extending through a flow passage 2 c , a flow-rate adjustment valve 20 , a flow passage 2 d , the flow passage 3 , the flow passage 4 , the flow passage 5 , and the flow passage 6 .
  • the flow passage 3 and the flow passage 5 are in thermal contact with the outer surface of the high-temperature-side wall portion 11 cd of the pulse tube 11 and the outer circumference surface of the heat radiating unit 12 .
  • the flow-rate adjustment valves 19 and 20 are provided in order to adjust the flow rate of refrigerant flowing through the branch circuit.
  • One or both of the flow-rate adjustment valves 19 and 20 may be omitted, depending on the flow resistances of the flow passage 2 c , the flow passage 2 d , the flow passage 3 , the flow passage 4 , the flow passage 5 , and the flow passage 6 .
  • the configuration of the remaining portion is identical with that of the first embodiment shown in FIG. 1 .
  • a portion of refrigerant flowing out from the discharge port 1 a of the pressure source 1 cools the high-temperature-side wall portion 11 cd of the pulse tube 11 and the heat radiating unit 12 , and then returns to the suction port 1 b of the pressure source 1 , without flowing into the cold reservoir 9 .
  • the discharge port 1 a of the pressure source 1 communicates with the high-pressure inlet port 7 a of the changeover valve 7 via the flow passage 2 a , the flow-rate adjustment valve 19 , and the flow passage 2 b .
  • a flow passage 32 divided from the flow passage 2 a communicates with the suction port 1 b of the pressure source 1 via a flow passage 33 , a flow passage 34 , a flow passage 35 , a flow passage 36 , the flow-rate adjustment valve 20 , and a flow passage 37 .
  • the flow passage 33 and the flow passage 35 are in thermal contact with the outer surface of the high-temperature-side wall portion 11 cd of the pulse tube 11 and the outer circumference surface of the heat radiating unit 12 , respectively.
  • the flow-rate adjustment valves 19 and 20 are provided in order to adjust the flow rate of refrigerant flowing through the flow passage 2 a and the flow passage 32 . Either or both of the flow-rate adjustment valves 19 and 20 may be omitted, depending on the flow resistances of the flow passage 32 , the flow passage 33 , the flow passage 34 , the flow passage 35 , the flow passage 36 , and the flow passage 37 .
  • the configuration of the remaining portion is identical with that of the first embodiment.
  • the refrigerator of the third embodiment has a greater refrigerating capacity as compared with that of the first embodiment, although the flow rate of the pressure source 1 increases.
  • a pulse tube refrigerator As shown in FIG. 4 , a pulse tube refrigerator according to a fourth embodiment, which belongs to the eighth invention, is characterized in that the high-temperature-side wall portion 11 cd of the pulse tube 11 and the heat radiating unit 12 are cooled by means of refrigerant flowing from a discharge port 41 a of a pressure source 41 differing from the pressure source 1 .
  • the discharge port 41 a of the pressure source 41 communicates with a suction port 41 b of the pressure source 41 via a flow passage 42 , a flow passage 43 , a flow passage 44 , a flow passage 45 , and a flow passage 46 .
  • the flow passage 43 and the flow passage 45 are in thermal contact with the high-temperature-side wall portion 11 cd of the pulse tube 11 and the heat radiating unit 12 , respectively.
  • the discharge port 1 a of the pressure source 1 communicates with the high-pressure inlet port 7 a of the changeover valve 7 via the flow passage 2 a .
  • the configuration of the remaining portion is identical with that of the first embodiment shown in FIG. 1 .
  • the refrigerator of the present embodiment has a greater refrigerating capacity at the low-temperature side of the pulse tube, as compared with that of the first embodiment, although the pressure source 41 must be newly provided.
  • a pulse tube refrigerator according to a fifth embodiment, which belongs to the sixth, seventh, eleventh, and eleventh inventions, is characterized in that cooling is performed by means of refrigerant flowing between the low-pressure output port 7 b of the changeover valve 7 and the suction port 1 b of the pressure source 1 .
  • the low-pressure output port 7 b of the changeover valve 7 communicates with the suction port 1 b of the pressure source 1 via a flow passage 52 , a flow passage 53 , a flow passage 54 , a flow passage 55 , a flow passage 56 , a radiator 57 which is air-cooled by a fan 59 , and a flow passage 58 .
  • the flow passage 53 and the flow passage 55 are in thermal contact with the high-temperature-side wall portion 11 cd of the pulse tube 11 and the heat radiating unit 12 , respectively.
  • the discharge port 1 a of the pressure source 1 communicates with the high-pressure inlet port 7 a of the changeover valve 7 via the flow passage 2 a .
  • the configuration of the remaining portion is identical with that of the first embodiment.
  • refrigerant flows from the cold reservoir 9 into the flow passage 53 via the low-pressure outlet port 7 b of the changeover valve 7 and the flow passage 52 , and cools the high-temperature-side wall portion 11 cd of the pulse tube 11 at the flow passage 53 . Subsequently, the refrigerant flows into the flow passage 55 via the flow passage 54 and cools refrigerant flowing between the phase adjuster 14 and the pulse tube 11 in the heat radiating unit 12 .
  • the timing of cooling the high-temperature side of the pulse tube shifts by about 180° as compared with the above-described fifth invention.
  • refrigerant flowing into the pressure source is lower in temperature than refrigerant flowing into the hot end of the cold reservoir, because refrigerant flowing out of the hot end of the cold reservoir flows. Therefore, the temperature of refrigerant which cools the high-temperature side of the pulse tube is low.
  • the embodiment of the fifth invention is superior, because in the present embodiment, the timing of cooling the high-temperature side of the pulse tube shifts by about 180° as compared with the fifth invention.
  • the wall of the pulse tube 11 is thick, the heat capacity increases, so that influence of the timing shift is mitigated by the heat accumulation effect of the wall, whereby refrigerating capacity is enhanced.
  • a pulse tube refrigerator is a type in which the pulse tube 11 is connected to the cold reservoir 9 and has a hot end 11 a that generates heat, wherein the cooling means 30 which cools a high-temperature-side wall portion of the pulse tube by means of cooling medium having a temperature lower than a high-temperature-side wall temperature of the pulse tube is constituted by the high-temperature-side wall portion 11 ed of the pulse tube provided in the atmosphere.
  • the discharge port 1 a of the pressure source 1 communicates with the high-pressure inlet port 7 a of the changeover valve 7 via the flow passage 2 .
  • the suction port 1 b of the pressure source 1 communicates with the low-pressure outlet port 7 b of the changeover valve 7 via the flow passage 18 .
  • the changeover valve 7 is controlled in such a manner that the port 7 c of the changeover valve 7 communicates with the high-pressure inlet port 7 a when refrigerant flows from the pressure source 1 to the cold reservoir 9 , and communicates with the low-pressure outlet port 7 b when refrigerant flows from the cold reservoir 9 to the pressure source 1 .
  • the cold reservoir 9 is filled with a cold-reserving material 9 c such as wire gauze.
  • the port 7 c communicates with the hot end 9 a of the cold reservoir 9 via the flow passage 8 .
  • the cold end 9 b of the cold reservoir 9 communicates with the cold end 11 b of the pulse tube 11 via the flow passage 10 .
  • the hot end 11 a of the pulse tube 11 communicates with the phase adjuster 14 via the heat radiating unit 12 and the flow passage 13 .
  • the high-temperature side 11 cd of the pulse tube 11 which constitutes the cooling means 30 , is disposed in the atmosphere outside the vacuum tank 15 , and the low-temperature side 11 de is disposed within the vacuum tank 15 .
  • the interior of the vacuum tank 15 is maintained at vacuum.
  • Refrigerant compressed at the pressure source 1 is cooled by means of a compressor cooler 100 .
  • the PV diagrams at the low temperature and high-temperature sides, respectively, of the pulse tube according to the sixth embodiment having the above-described configuration are the same as those of the first embodiment shown in FIG. 6 .
  • the high-temperature-side wall portion 11 cd of the pulse tube 11 Since the temperature of the high-temperature-side wall portion 11 cd of the pulse tube 11 is higher than the temperature of surrounding air, the high-temperature-side wall portion 11 cd of the pulse tube is cooled by the surrounding air, whereby the high-temperature-side wall portion 11 cd captures heat from a portion of refrigerant in contact with the inner surface thereof to thereby lower the temperature of the refrigerant.
  • a pulse tube refrigerator according to a seventh embodiment is characterized in that a large number of annular fins 21 and 22 are provided on the high-temperature-side wall portion 11 cd of the pulse tube 11 provided in the atmosphere outside the vacuum tank 15 and on the heat radiating unit 12 , respectively.
  • the large number of annular fins 21 and 22 are arranged on the outer circumferential surfaces of the pulse tube 11 and the heat radiating unit 12 at constant intervals along the axial direction, as shown in FIG. 8 .
  • the pulse tube refrigerator according to the seventh embodiment has an increased conduction surface, whereby cooling of the high-temperature-side wall portion 11 cd of the pulse tube 11 and the heat radiating unit 12 can be performed better than in the sixth embodiment shown in FIG. 7 .
  • the refrigerating quantity increases, as compared with the sixth embodiment.
  • a large number of the fins 21 and 22 are fixed to the outer circumferential surface of the high-temperature-side wall portion 11 cd of the pulse tube 11 and the outer circumferential surface of the heat radiating unit 12 at proper intervals.
  • a fin may be provided spirally on the outer circumferential surface of the high-temperature-side wall portion 11 cd of the pulse tube 11 and the outer circumferential surface of the heat radiating unit 12 .
  • a pulse tube refrigerator according to an eighth embodiment is characterized in that a large number of vertical fins 31 and 32 are provided on the high-temperature-side wall portion 11 cd of the pulse tube 11 provided in the atmosphere outside the vacuum tank 15 and on the heat radiating unit 12 , respectively.
  • the large number of vertical fins 31 and 32 are arranged on the outer circumferential surfaces of the pulse tube 11 and the heat radiating unit 12 at constant intervals along the circumferential direction, in such a manner that the fins 31 and 32 extend over the entire lengths of the pulse tube 11 and the heat radiating unit 12 , as shown in FIG. 9 .
  • the pulse tube refrigerator according to the eighth embodiment has an increased conduction surface, whereby cooling of the high-temperature-side wall portion 11 cd of the pulse tube 11 and the heat radiating unit 12 can be performed better than in the sixth embodiment.
  • the refrigerating quantity increases, as compared with the sixth embodiment.
  • a pulse tube refrigerator As shown in FIG. 10 , a pulse tube refrigerator according to a ninth embodiment is characterized in that air is forcedly caused to flow toward the high-temperature-side wall portion of the pulse tube and a pressure generation means 24 such as a fan is provided in the vicinity of the high-temperature-side wall portion 11 cd and the heat radiating unit 12 .
  • the high-temperature-side tube portion 11 cd of the pulse tube 11 disposed in the atmosphere is formed of a material 25 which has good heat conduction
  • a low-temperature-side tube portion 11 bd of the pulse tube 11 disposed within the vacuum tank 15 is formed of a material 26 which has poor heat conduction.
  • the high-temperature-side tube portion 11 cd and the low-temperature-side tube portion 11 bd are joined together.
  • the material 25 which has good heat conduction, is copper, aluminum, or the like, and the material 26 , which has poor heat conduction, is stainless steel or the like.
  • the high-temperature-side tube portion of the pulse tube disposed in the atmosphere provides a high degree of heat conduction in the radial direction, whereby the temperature difference between the inner circumferential surface and the outer inner circumferential surface of the high-temperature-side tube portion decreases, the temperature of refrigerant in contact with the inner circumferential surface decreases, and the refrigerating capacity increases.
  • one end of a conduction member 30 is brought into thermal contact with the high-temperature-side wall portion 11 cd of the pulse tube 11 , and the other end of the conduction member 30 is brought into thermal contact with the vacuum tank 15 .
  • the high-temperature-side wall portion 11 cd of the pulse tube 11 is cooled, via the conduction member 30 , by means of the vacuum tank 15 , which serves as a cooling source whose temperature is lower than the temperature of the high-temperature-side wall portion 11 cd thereof, whereby the refrigerating capacity is increased.
  • the high-temperature-side wall portion 11 cd of the pulse tube 11 may be disposed inside the vacuum tank or in the atmosphere outside the vacuum tank.
  • the phase adjuster 14 used in the above-described embodiment may be of an orifice type shown in FIG. 13(A) , an active buffer type shown in FIG. 13(B) , a double-inlet type shown in FIG. 13(C) , a 4-valve type shown in FIG. 13(D) , or the like.
  • the pulse tube refrigerators are of a single stage type; however, the present invention is not limited thereto, and can be applied to pulse tube refrigerators having two or more stages.
  • the cooling means cools a high-temperature-side wall portion of the pulse tube by use of refrigerant of a pulse tube refrigerator, the temperature of the high-temperature-side wall portion of the pulse tube decreases. As a result, the quantity of heat which reaches the cold end of the pulse tube because of heat conduction decreases. In addition, since a portion of refrigerant gas in contact with the inner surface of the high-temperature-side wall portion of the pulse tube is cooled, the quantity of heat which reaches the cold end of the pulse tube because of movement of the refrigerant gas decreases. As a result, the refrigerating capacity is increased.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US10/486,355 2001-08-30 2002-08-29 Pulse tube refrigerating machine Expired - Fee Related US7047750B2 (en)

Applications Claiming Priority (3)

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JP2001262282A JP4766800B2 (ja) 2001-08-30 2001-08-30 パルス管冷凍機
JP2001-262282 2001-08-30
PCT/JP2002/008733 WO2003019087A1 (fr) 2001-08-30 2002-08-29 Machine de refrigeration pour tube de pulsation

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US7047750B2 true US7047750B2 (en) 2006-05-23

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US (1) US7047750B2 (fr)
EP (1) EP1431682A4 (fr)
JP (1) JP4766800B2 (fr)
CN (1) CN1628232A (fr)
RU (1) RU2273808C2 (fr)
WO (1) WO2003019087A1 (fr)

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US20060174635A1 (en) * 2005-02-04 2006-08-10 Mingyao Xu Multi-stage pulse tube with matched temperature profiles
US20110146302A1 (en) * 2009-12-21 2011-06-23 Newman Michael D Cryogenic heat exchanger for thermoacoustic refrigeration system

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US8671698B2 (en) * 2007-10-10 2014-03-18 Cryomech, Inc. Gas liquifier

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US20050044860A1 (en) 2005-03-03
EP1431682A4 (fr) 2009-02-25
JP4766800B2 (ja) 2011-09-07
RU2004107857A (ru) 2005-05-20
JP2003075001A (ja) 2003-03-12
WO2003019087A1 (fr) 2003-03-06
CN1628232A (zh) 2005-06-15
RU2273808C2 (ru) 2006-04-10
EP1431682A1 (fr) 2004-06-23

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